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WO2001055583A2 - Injecteur - Google Patents

Injecteur Download PDF

Info

Publication number
WO2001055583A2
WO2001055583A2 PCT/DE2001/000100 DE0100100W WO0155583A2 WO 2001055583 A2 WO2001055583 A2 WO 2001055583A2 DE 0100100 W DE0100100 W DE 0100100W WO 0155583 A2 WO0155583 A2 WO 0155583A2
Authority
WO
WIPO (PCT)
Prior art keywords
injection nozzle
nozzle needle
control chamber
nozzle
nozzle according
Prior art date
Application number
PCT/DE2001/000100
Other languages
German (de)
English (en)
Other versions
WO2001055583A3 (fr
Inventor
Dieter Kienzler
Wolfgang Stoecklein
Friedrich Boecking
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2001055583A2 publication Critical patent/WO2001055583A2/fr
Publication of WO2001055583A3 publication Critical patent/WO2001055583A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to an injection nozzle for a fuel injection system, in particular for a so-called Commo ⁇ -Rail system, which is provided with a piezo actuator.
  • a control chamber in which a control fluid, usually part of the fuel to be injected, can be accumulated in a controlled manner.
  • a control piston projects into the control chamber and, at its end facing away from the control chamber, cooperates with a nozzle needle of the injection nozzle.
  • the piezo actuator interacts with a valve element that can open or close a fluid outlet from the control room. When the fluid outlet from the control chamber is closed, the fluid accumulated there creates a pressure which acts on the control piston and holds the nozzle needle in the closed position. If, on the other hand, the fluid drain from the control chamber is opened by the valve element, the fluid can flow out of the control chamber, so that the pressure drops there.
  • the object of the invention is to provide an injection nozzle which is of particularly simple construction, which, when the nozzle needle is actuated, produces a high nozzle needle speed and thereby enables a pre-injection with small pre-injection quantities and finally has a reduced fuel leakage.
  • a fuel injector according to the invention with the features of claim 1 has a simple structure, since the previously required control piston can be dispensed with; the nozzle needle protrudes directly into the control room.
  • the piezo actuator enables very short switching times, so that a very short opening of the nozzle needle and a correspondingly small injection quantity are possible, for example for a pre-injection.
  • By dispensing with the control piston only smaller masses have to be moved when opening and closing the nozzle needle, so that there is a higher nozzle needle speed. If the valve element is in the closed position, there is no leakage.
  • 1 shows a schematic section of an injection nozzle according to a first embodiment of the invention
  • 2 shows a schematic section of an injection nozzle according to a second embodiment of the invention
  • FIG. 3 shows a schematic section of an injection nozzle according to a third embodiment of the invention
  • 4 shows a schematic section of an injection nozzle according to a fourth embodiment of the invention.
  • FIG. 5 shows a schematic section of a nozzle needle for an injection nozzle according to a fifth embodiment of the invention.
  • FIG. 1 shows an injection nozzle according to a first embodiment. It has a nozzle body, generally designated by the reference numeral 10, in which a nozzle needle 12 is slidably arranged.
  • the nozzle needle is slidable between a closed position, in which the injection openings 14 are closed, and an open position, in which the injection openings are released, so that fuel can be injected, which is supplied via a supply bore 16, the nozzle needle 12 projects with it from the end facing away from the injection openings 14 into a control chamber 18 which is connected to the supply bore 16 via a fluid inlet 20 which is provided with an inlet throttle 21.
  • a mechanical closing spring 22 is arranged in the control chamber 18, which is designed here as a compression spring and acts on the nozzle needle 12 in its closed position.
  • a stroke stop 24 for the nozzle needle 12, shown schematically here, is arranged in the interior of the control chamber 18.
  • a valve seat 28 is formed in the fluid drain, with which a valve element 30 can interact. If the valve element 30 bears against the valve seat 28, the outlet from the control chamber 18 is closed, and if the valve element 30 is lifted off the sealing seat, this can occur in the control chamber 18. jammed fluid flow through the fluid outlet 26 to a fuel return 32.
  • the inlet throttle 21 and the outlet throttle 27 are dimensioned such that the fluid flows out of the control chamber 18 faster than it can flow in.
  • a second valve seat can be arranged on the side of the fluid outlet 26, so that a double-switching valve element is formed.
  • the valve element 30 can then be transferred from a first closed position, for example in contact with the valve seat 28, via an open middle position, in which it is not in contact with either of the two valve seats, to a second closed position in contact with the second valve seat.
  • the valve element 30 is actuated by a piezo actuator 34 which is arranged at the end of the injection nozzle facing away from the nozzle needle 12.
  • the piezo actuator acts on an input piston 36, which acts on an output piston 40 via a hydraulic coupling chamber 38.
  • the output piston 40 is finally connected to the valve element 30, a return spring 42 being provided, which presses the valve element 30 into its closed position and the output piston 40 against the piezo actuator.
  • the hydraulic coupling space together with the input and output pistons serves to translate the comparatively small stroke of the piezo actuator into a larger stroke of the valve element 30.
  • the valve element 30 When the piezo actuator is not actuated, the valve element 30 is closed, so that the fuel, which is supplied via the supply bore 16 and is under high pressure, is accumulated in the control chamber 18.
  • the cross section of the nozzle needle 12 in the control chamber 18 is dimensioned such that the closing force generated there when the fuel is pent-up is greater than the opening force generated by the fuel pressure present at the front end of the nozzle needle.
  • the piezo actuator is actuated so that the valve element 30 is lifted off the valve seat 28.
  • the control chamber 18 is connected to the fuel return 32; there is a leakage current.
  • the opening force acting on the nozzle needle becomes greater than the closing force, so that the nozzle needle is opened.
  • valve element 30 is first brought back into contact with the valve seat 28. As a result, the fuel supplied via the fluid inlet 20 is accumulated again in the control chamber 18, so that the closing force generated there causes the nozzle needle to close.
  • control chamber 18 is comparatively large, so that it represents a relatively soft hydraulic system. The result of this is that there is only a delayed drop in the pressure in the control chamber 18 when the valve element 30 is opened. It follows from this that, with the control duration remaining the same, pre-injection quantities result which, in any case, are not larger in comparison with the previous systems. If a double-switching valve element is used, even shorter switching times of the valve element result in connection with the piezo actuator 34. This enables smaller pre-injection quantities to be achieved than before.
  • Another important feature of the injection nozzle according to the invention is that a high nozzle needle speed is achieved when the nozzle needle is closed.
  • the needle speed is largely determined by the required stroke volume, that is to say the area of the nozzle needle in the control chamber 18 and the nozzle needle stroke. This fluid volume must flow into the control chamber 18 via the inlet throttle 21. The smaller this stroke volume with the same cross section of the inlet throttle 21, the more the nozzle needle speed is greater.
  • the closing movement of the nozzle needle is supported by the mechanical closing spring 22, which, with sufficient dimensioning, already ensures strong acceleration of the nozzle needle and thus a high nozzle needle speed.
  • FIG. 2 shows an injection nozzle in accordance with a second embodiment.
  • the same reference numerals are used for the components known from the first embodiment, and reference is made to the above explanations.
  • a compensating piston 44 is arranged in the control chamber 18, which abuts the nozzle needle 12 at one end and projects into a compensating chamber 46 at the other end, which is guided in the nozzle body 10.
  • the compensation chamber 46 is connected to the supply bore 16 via a fluid inlet so that it is supplied with pressurized fluid.
  • the mechanical closing spring 22 is supported on the compensating piston 44, so that the nozzle needle 12 is acted upon indirectly.
  • the advantage of this embodiment is that the fluid volume that is displaced when the nozzle needle 12 is moved is reduced compared to the first embodiment, specifically in accordance with the cross section of the compensating piston in the region of the guide through the nozzle body 10 the fluid volume displaced is the effective area involved in the stroke; this is composed of the cross-sectional area of the nozzle needle 12 reduced by the cross-sectional area of the compensating piston 44 in the region of the guidance through the nozzle body 10.
  • FIG. 3 shows an injection nozzle in accordance with a third embodiment.
  • the same reference numerals are used for the components which are known from one of the preceding embodiments, and reference is made to the above explanations.
  • the end of the compensating piston 44 facing away from the nozzle needle 12 does not end in a compensating chamber, but in a spring chamber 50 which is closed.
  • the oil spring formed by the compensating piston 44 and the spring chamber 50 has a comparatively high rigidity c, which is calculated as follows:
  • E is the modulus of elasticity of the oil
  • A the effective piston area
  • V the spring chamber volume
  • a closing spring with high rigidity is advantageous. This makes it possible to provide a comparatively low pretension when the nozzle needle is closed, while a large closing force then results when the nozzle needle is open.
  • the closing force acting on the spring is composed of the pretensioning force when the nozzle needle is closed and the product of the nozzle needle stroke and spring stiffness c.
  • a mechanical spring with high rigidity could be used to obtain a high closing force.
  • such requires a relatively large space, so that the control room 18 should have a very large volume. This would also impair the function of the injection nozzle, since this would result in a slower pressure relief and a slower pressure build-up in the control room.
  • the hydraulic closing spring formed by the spring chamber 50 and the compensating piston 44 offers the desired great rigidity, so that an injection nozzle with a small mechanical closing spring can be realized; the mechanical closing spring only has to provide a slight pretension when the nozzle needle is not open. In this way, a small volume of the control room 18 can be realized. At the same time, a large closing force is achieved when the nozzle needle is open due to the great rigidity of the hydraulic spring. Due to the low pretension of the nozzle needle when closed, the nozzle needle opens quickly when actuated. The small control chamber 18 results in good control behavior of the nozzle needle. The high closing force with the nozzle needle open) results in the desired high accelerations and high nozzle needle speeds when closing.
  • Injection nozzle shown according to a fourth embodiment of the invention.
  • the same reference numerals are used for the components known from the previous embodiments, and reference is made to the above explanations.
  • the mechanical closing spring 22 is no longer arranged in the control chamber 18, but in the compensation chamber 46. It is supported on a spring plate 52 on the compensating piston 44 and thereby acts indirectly on the nozzle needle 12 in its closed position.
  • a mechanical closing spring with high rigidity can be used to generate a high closing force in the open state despite the low pretension when the nozzle needle is closed.
  • such a mechanical closing spring with high rigidity is used without the control chamber 18 therefore having to be made correspondingly large. Due to the arrangement of the mechanical closing spring 22 which is separate from the control chamber 18, the closing spring can now be designed with the desired rigidity without the design of the control chamber 18 being influenced thereby.
  • the control chamber 18 can thus be designed solely with regard to the desired hydraulic behavior when opening and closing the valve element 30, in particular with a small volume, so that there is a direct response behavior of the injection nozzle.
  • the fluid inlet 48 can also be omitted in the design according to the fourth embodiment, so that a spring chamber is formed, as is known from the third embodiment, but in which the mechanical closing spring 22 is arranged. Both the mechanical and the hydraulic closing spring are thus combined, and the control chamber 18 can be designed solely in view of the hydraulic conditions.
  • FIG. 5 shows the front end of an injection nozzle according to a fifth embodiment.
  • the fluid inlet 20 and the inlet throttle 21 are not formed in the nozzle body 10, but instead extend through the nozzle needle 12 starting from an annular space 54, which is supplied with pressurized fuel via the feed bore 16 and from which the fuel is open when it is open Nozzle needle 12 flows to the injection openings 14. Since the inlet throttle and the outlet throttle) are now arranged in different components, namely the inlet throttle 21 in the nozzle needle 12 and the outlet throttle 27 in the nozzle body 10, there are considerable advantages with regard to the pairing possibilities of the two components during manufacture.
  • the design of the nozzle needle 12 shown in FIG. 5 can of course also be used in the injection nozzles shown in FIGS. 1 to 4.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

L'invention vise à créer un injecteur doté d'un actionneur piézo-électrique, qui présente une construction simple et permet d'obtenir de faibles quantités injectées grâce à des temps d'ouvertures courts. A cet effet, l'injecteur comporte : un corps (10) d'injecteur ; une pointe (12) d'injecteur mobile dans ce dernier ; un compartiment de commande (18), dans lequel une extrémité de la pointe d'injecteur pénètre et qui est alimenté en fluide sous pression par l'intermédiaire d'une entrée de fluide (20) ; une soupape de commande (28, 30, 34) dotée d'un élément soupape (30) pouvant ouvrir et fermer une sortie de fluide (26) du compartiment de commande (18) ; un actionneur piézo-électrique (34) qui peut actionner l'élément soupape (30).
PCT/DE2001/000100 2000-01-26 2001-01-12 Injecteur WO2001055583A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000103252 DE10003252A1 (de) 2000-01-26 2000-01-26 Einspritzdüse
DE10003252.4 2000-01-26

Publications (2)

Publication Number Publication Date
WO2001055583A2 true WO2001055583A2 (fr) 2001-08-02
WO2001055583A3 WO2001055583A3 (fr) 2001-12-06

Family

ID=7628746

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2001/000100 WO2001055583A2 (fr) 2000-01-26 2001-01-12 Injecteur

Country Status (2)

Country Link
DE (1) DE10003252A1 (fr)
WO (1) WO2001055583A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE375446T1 (de) 2004-01-13 2007-10-15 Delphi Tech Inc Kraftstoffeinspritzventil
DE102005004206A1 (de) * 2005-01-29 2006-08-03 Bayerische Motoren Werke Ag Fernbedieneinrichtung für Kraftfahrzeuge
DE102010047940B4 (de) * 2010-10-08 2019-03-14 Tdk Electronics Ag Anordnung eines Piezoaktors

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5713326A (en) * 1995-05-03 1998-02-03 Institut Fur Motorenbau Prof. Huber Gmbh Injection nozzle
DE19744235A1 (de) * 1997-10-07 1999-04-08 Fev Motorentech Gmbh & Co Kg Einspritzdüse mit piezoelektrischem Aktuator
DE19844996A1 (de) * 1998-09-30 2000-04-13 Siemens Ag Vorrichtung und Verfahren zur Dosierung von Fluid

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5713326A (en) * 1995-05-03 1998-02-03 Institut Fur Motorenbau Prof. Huber Gmbh Injection nozzle
DE19744235A1 (de) * 1997-10-07 1999-04-08 Fev Motorentech Gmbh & Co Kg Einspritzdüse mit piezoelektrischem Aktuator
DE19844996A1 (de) * 1998-09-30 2000-04-13 Siemens Ag Vorrichtung und Verfahren zur Dosierung von Fluid

Also Published As

Publication number Publication date
WO2001055583A3 (fr) 2001-12-06
DE10003252A1 (de) 2001-08-09

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